Control device for programmed regulation of hydraulic fluid-operated traverse mechanisms of spooling, spinning and especially ring twist machines



N v- 22, 1955 H. SCHIPPERS ETAL 3,236,941

CONTRQL DEVICE FOR PROGRAMMED REGULATION OF HYDRAULIC FLUID-OPERATED TRAVERSE MECHANISMS OF SPOOLING, SPINNING AND ESPECIALLY RING TWIST MACHINES 2 Sheets-Sheet 1 Filed Dec. 21, 1964 INVENTORSI HEINZ SCHIPPERS KARL BAUER HERBERT TURK mid/ ag 04%, wow;

ATT'YS N 1965 H. SCHIPPERS ETAL 3, 86,9

CONTROL DEVICE FOR PROGHAMMED REGULATION OF HYDRAULIC FLUID-OPERATED TRAVERSE MECHANISMS OF SPOOLING,

SPINNING AND ESPECIALLY RING TWIST MACHINES 21. 1964 2 Sheets-Sheet 2 Filed Dec.

ATT'YS S W. K DH R U WE T k i I m y CA T n R 5 E i. @v? m R R 7 A E H K H M FIG. 7

gw a 60% a United States Patent Claims. ci. 242-26.1)

The invention relates to control devices for the programmed regulation of hydraulic fluid-operated traverse mechanisms of spooling, spinning and especially ring twist machines, which devices serve the purpose of modifying the flowing amount of the hydraulic fluid and thereby the traverse speed in dependence on driven cam control elements according to a predetermined program.

Hydraulic traverse gears in which the traverse motion is accelerated or retarded according to a certain program in each stroke are used in various types of spooling, spinning and ring twist machines. There it is usual practice to achieve such stroke accelerations or retardations by modification of the amount of flowing fluid of the hydraulic drive, which in turn determines the traverse speed. As is well known, the modification of the amount of the flowing, hydraulic pressure fluid is possible in various ways, as, for example, by controlled modification of the amount of hydraulic fluid pumped per second or by use of so- L called fluid quantity regulators or chokes.

In a known hydraulic fluid drive, the pump of the hydraulic drive is controlled by a template which is rigidly attached to the working piston rod generating the main stroke. In this system the entire drive aggregate for the (3 main stroke, consisting of pump, fluid container, line system and the main cylinder of the working piston for the main stroke, together with corresponding control devices, is raised or lowered by the whole length of the winding body during its build-up by a separate drive.

means of a short main stroke a conical-form yarn layer,

of which several distributed axially one upon another by sub-strokes yield the complete winding body.

Another hydraulic traverse device has a continuously adjustable quantity regulator mounted in fixed position between pump and control valve for the working cylinder, which regulator controls the amount of pressure fluid introduced on both sides of the working piston in the time unit for the purpose of modifying the traverse stroke speed. The control of the continuously adjustable quantity regulator is accomplished over a guide plate of the cam type, a kind of template which is connected rigidly with the piston rod of the working piston. With this device only such yarn winding bodies can be produced wherein, for their build-up, the traverse stroke remains always equal and is not axially shifted.

Similarly, there exists another control device in which an adjustable linear control edge for the stationary quantity regulator is likewise attached rigidly to the working piston rod. The constructive measures proposed for this, however, are obviously not suited also in those cases in which a stroke displacement is needed for the winding formation to fulfill the requirement often demanded in practice, namely that, for example, in the case of the so-called deck winding, that is, winding with conical portions at both ends of the wound package,

ice

with a great, constantly reciprocating main stroke of more than 50% of the total winding body length and a small sub-stroke going back or forth only once during the winding formation at the end of each main stroke there is achieved over a limited distance a certain acceleration with equal absolute end velocity. In order to achieve this, it would be necessary during the entire winding buildup with stroke displacement to assure an analogous or even equal velocity characteristic for each individual stroke. This, however, is impossible with the above-described control device because, in the stroke displacement for the working piston of the hydraulic cylinder a cam element participates in the stroke displacement movernent. The cam element is shifted With respect to a stationary setting member of the quantity regulator. The stationary setting member contacts or feels out the curve of the cam element. In the course of the stroke displacement, the setting member passes into another control range or out of the control range of the cam element.

The invention has as its basis the avoidance of the above-enumerated drawbacks of the known system and the discovery of control devices with the aid of which all the desired variations of the usual traverse systems can be executed, especially those with stroke displacement and with equal velocity characteristics recurring in each stroke.

In order to achieve these objectives, it is proposed according to the invention that the control element or elements executed in curve or cam form be mounted so as to be rotatable or slidable with respect to their indirect or direct drive element and be provided with stop surfaces or members which cooperate adjustably with a stationary stop in each case for the purpose of limiting the effective curve path of the control element. The curve-type control element can be connected with the drive element via a disengageable coupling which is disengaged at the end of each base stroke and thereby at the beginning of the substroke distance belonging to each base stroke. Alternatively, the control element itself can be equipped with such a coupling device, which may consist, for example, of a magnetic coupling or a spring-biased clutch for the drive element.

Insofar as the curve-type control element, as in the known executions, is driven indirectly or directly through the piston rod of the hydraulic cylinder, as hitherto usual, it participates in each case in its reciprocating traverse movement in the main stroke, in which it undergoes either a longitudinal movement or a corresponding rotary movement. Since it is, however, according to the invention, mounted rotatably or slidably with respect to its drive element, it can be held back upon disengagement of the coupling device for the stroke displacement span of the total stroke movement of the working piston going beyond the base stroke whereby it constantly retains its set position with the prescribed control range with respect to the curve and the stationary setting member of the quantity regulator feeling out this curve, despite progressive excursion of its drive element with increasing development of the substroke. The same undesired displacement or excursion manifestations would also occur if the curve-type control element is driven not by the piston rod of the hydraulic cylinder but, for example, by the ring bench or a separate drive of its own. Here, too, there is needed, therefore, the executions according to the invention of the control devices.

In order to be able to execute the arrangement of the control devices with as much space saving as possible, it is further proposed according to the invention that the control element be executed as a cam plate which is connected with its drive element by means of a slip coupling. The torque or the frictional force to be transmitted by the 3 slip coupling can be adjustable by having the slip coupling constructed or made adjustable or settable by dimensioning or varying of the spring force engaging at the drive element in such a way that the torque or other frictional drive force to be transmitted by it is, on the one hand, just great enough to exercise in the main stroke the shifting forces necessary for the operation of the quantity regulating apparatus or of its setting member, but, on the other hand, is low enough so that in the strikingof the cooperating limiting stops in the substroke the frictional drive force of the coupling is overcome. In order, finally, to change the cam plate for one of another curve characteristic and thereby to be able to-achieve another winding size or length or type of winding at another velocity course, either the cam plate on the slip coupling or the cam plate together with the slip coupling on the drive shaft can be provided in interchangeable or commutable or shiftable form. In the same way, the cooperating limiting stops on the cam plate or on the machine frame can be provided in interchangeable or commutable or shiftable form.

By means of the apparatus according to the invention, it is, moreover, possible without additional expenditure, also to wind spool bodies as those whose structure results through so-called stroke reduction or, vice versa, through stroke increase. It is just as simple to alternate within a winding operation layers resulting by stroke reduction with those which have resulted through stroke increase, in a certain rhythm with one another. Number and thickness of the successive layers of the one and the other type can be altogether difierent. The especially noteworthy feature of the invention lies in that, with its aid in the above-described winding process to each individual stroke, whether short or long, during a constantly equally long section, there can be imparted an equal course of acceleration. This advantage is made possible by the feature that the effective curve path of the control element is in each case shorter than the shortest traverse stroke occurring whereby quite surely at the begining of each new stroke the determinative curve path has in each case assumed its sole correct starting position for the speed control of this stroke. For this purpose it will sufiice, therefore, if before the commencement of the shortest stroke, the stop surfaces or members limiting the curve courses strike upon their appertaining stop pins or the like and both control elements which carry the curved control surfaces can be turned or thrust by a certain amount in addition with respect to their drive element until the stroke direction is finally reversed.

For the production of the last-described winding forms, it has proved especially advantageous to provide a single curve-type control element which carries two effective control cams for the controlling of two quantity regulating devices. This arrangement proves especially economical, moreover, both in space requirement and also in cost expenditure. In addition, this arrangement allows to superimposed on one another the ranges of like functions of the two cam surfaces.

In further development of the invention, a solution was found which provides a controlled modification of the speed characteristic of the individual strokes in the course of the whole winding process. The magnitude of the acceleration or of the retardation as well as the length of the acceleration or retardation section during the particular stroke can, accorrdingly, be modified through the feature that for the superimposing of control movements the quantity regulating device or devices are arranged so as to be additionally adjustably set in the direction toward the cam control curve or away from it.

The control devices of this invention have, over the known arrangements, especially the advantage that they operate completely reliably and in the case of traverse problems with periodically outgoing and/ or incoming substroke or in the case of stroke enlargement and/ or stroke reduction during the whole-winding process, they assure exactly the same speed characteristics for each individual Even in the case of very long winding processes.

stroke. such as are usual in the winding of synthetic threads of very fine or maximally fine denier, winding faults, otherwise so much feared, will no longer occur. It is possible by means of the control device to produce practically all the usual winding types with programmed speed charac-.

teristics, and in particular those in which especially high demands are placed on the trueness to measure of the FIG. 1 is a schematic view, partly in section, of a hy-.

draulically driven traverse device with two adjustable quantity regulators for reciprocating a ring bench of a ring twist machine. a

FIG. 2 is a detailed side elevation of one of the two quantity regulators controlled by means of a rotatable cam plate.

FIG. 3 is a section through section 3-3 of the cam plate and its coupling with the drive shaft according to FIG. 2.

FIG. 4 is a schematic side elevation, partly in section, of a quantity regulator adjustable by means of a longitudinally slidable mounting on a hydraulic piston rod.

FIG. 5 is a schematic side elevation, partly in section, of a similar cam plate mounted on a hydraulic piston rod by means of a different coupling.

FIG. 6 is a perspective view of a rotatable cam plate with an asymmetric control cam edge.

FIG. 7 is a perspective view of a rotatable cam plate with two oppositely situated control cam edges in combination with two quantity regulators and the cam followers thereof.

In a ring twist machine,.the raising and lowering of the ring bench or spindle bench necessary for the buildup of a winding of a certain type is accomplished by means of the traverse device which transmits its programcontrolled reciprocating movement over connecting members to the bench to be moved.

In the embodiment represented in FIG. 1, the hydraulically driven traverse mechanism consist-s essentially of the ring bench 1 suspended on cables 2. The cables run over deflection rollers 3 and are attached at their other end to the piston rod 4 of the working piston 6 in the hydraulic cylinder 5.: On the piston rod 4 there is mounted the switching feeler ,7, which actuates the stroke limiting switches or end switches 8,9 and 10 for the traverse movements, which, in turn, are shifted on the guide rod 12 by conveyor members (not represented) of the mechanically, hydraulically or electrically controlled program control system 11.

The usual hydraulic control elements necessary for the control of the operating piston 6, for example, the reversing slider and the pressure setting valve (not shown in detail) are accommodated in the common casing 13. The hydraulic fluid is conveyed by the pump 14'from'the supply tank 15 into the hydraulic drive system and flows over the return line 16 back into the supply tank. The lines 18 and 18', 20 and 20 connect the quantity regulators 21 and 22 and the lines 17 and 19 the hydraulic cylinder 5 with the other hydraulic control elementsin the casing 13.

On the piston rod 4 of the working piston 6 there is rigidly secured by means of the holding arm 23 a toothed rack '24. The gear wheel 26 fixed on the shaft 15 engages the toothed rack 24. The shaft 25 is journalled rotatably in the bearings 27 and 28 and carries on its free end the slip couplings 29 and 30 on which the-re are attached as cam-type control elements the cam plates 31 and 32. The rolls 35 and 36 of the adjusting slides 33 and 34 of the quantity regulators 21 and 22 are pressed by springs (not shown) against the surfacesof 1 Resulting from1the accumulation .of min-onfaults.

the cam plates 31 and 32. Referring to FIG. 2, the removable stop clamps 37 and 38 secured on the cam plate 31 are illustrated with the stop clamp 37 shown in position against the fixed stop pin 39. The stop clamp 38, especially on reversal of the sub-stroke direction, can cooperate correspondingly with the fixed stop pin 39'. In FIG. 1, the stop clamps both on the cam plate 31 and also on the cam plate 32 are omitted for the sake of perspicuity, and only the stationary stop pin pairs 39 and 39' and 40 and 40', respectively, are represented.

Referring to FIG. 3, the control element, the annular cam plate 31, is attached by means of screws 41 on a central and coaxial friction disk 42 which, via a pressure washer 43, is pressed by coil spring 44 against the collar 45 of a shaft sleeve 46, on the other end of which there is screwed the spring sleeve 47 serving as counterbearing for the spring 44. A nut 48 secures the spring sleeve 47 on the shaft sleeve 46, which, in turn, is held by the nut 49 on the shaft 25. The. friction disk 42 of the cam plate 31, under urging of a certain force, the level of which is dependent on the pressure applied by the spring 44, can turn with respect to the shaft sleeve 46. By means of fitting keys the .pressure washer 43 is secured with respect to the shaft sleeve 46 and this, in turn, with respect to the shaft 25 against twisting,

During operation, the conveyor pump 14 sucks the pressure fluid from the supply tank and presses it into the hydraulic drive system. If the working piston 6 is to move to the left, the pressure fluid is conducted from the hydraulic control elements arranged in the casing 13, with by-passing of the line leading to the quantity regulator 21, directly over line 19 into the righthand side of the hydraulic cylinder 5. The pressure fluid emerging from the left-hand side of the hydraulic cylinder 5 flows over lines 17 and 18 through the quantity regulator 22, the line 18' and over the control elements in the casing 13 through the return flow 16 back into the supply tank 15. The working piston 6, moving to the left, drives the piston rod 4 and the cables 2 running over the deflection rollers 3, and raises the ring rail 1.

Working piston 6 and piston rod 4 move to the left until the switching feeler 7 actuates the stroke limiting switch 8, through the contact-giving of which the control elements in casing 13 are reversed, so that the hydraulic fluid now is conveyed from the pump 14 over the corresponding control elements directly through line 17 into the left-hand side of the hydraulic cylinder 6. The working piston 6 is thereby thrust to the right, in which process the fluid emerging from the right-hand side of the hydraulic cylinder 5 flows back over the lines 19 and 20, the quantity regulator 21, the line 20' and over the control elements in casing 13 through the return line 16 back into the supply tank 15. The piston rod 4 moves likewise to the right, whereby the ring rail 1 is lowered until the switching feeler 7 actuates the stroke limiting switch 9.

The corresponding hydraulic control elements are hereby again reversed in order to reverse the direction of the working piston stroke.

In each phase of the ring rail stroke, the stroke speed is determined by the amountof pressure fluid flowing through the quantity regulator 22 or 21 in the time unit, which amount, in turn, is continuously regulated by the adjusting slides 34 and 33, respectively, controlled by the cam plates 32 and 31, respectively. This amount of pressure fluid flowing through the quantity regulator 22 or 21 can be infinitely varied between a minimal and a maximal amount. With the adjusting slides 33 or 34 slid entirely into the casing, the flow amount is smallest, and can, if need be, even amount to zero. The flowthrough amount is greatest when the adjusting slide 33 or 34 projects farthest from its respective quantity regulating casing. To each curve point of the cam plate 31 or 32 there corresponds a quite definite position of the adjusting slide 33 or 34 and thereby a quite definite flow amount ofthe quantity regulator 21 or 22.

In the production of a yarn winding body, the buildup of which takes place through displacement of the ring rail main stroke, the two stroke limiting switches 8 and 9 in the example represented slide slowly to the left with constant separation spacing and constant speed. Thereby the position of the fundamental stroke of the ring rail is shifted gradually upward and that of the working piston to the same degree toward the left. The toothed rack 24 secured by means of the holding arm 23 on the piston rod 4 has the same stroke length and stroke position as the working piston 6. The angle by which the gear wheel 26 is turned forward at each stroke is, in the case of continuous stroke displacement, always equal. The engagement stretch of the toothed rack (that is, the stretch on the toothed rack whose teeth engage with the teeth of gear wheel 26 during a stroke) moves, however, slowly to the right and the engagement arc of the gear wheel is shifted correspondingly on its circumference, because the backward stroke, due to the progressive stroke displacement, is somewhat smaller than the forward stroke. If the stroke displacement takes place not continuously, but stepwise, then the difference between for- Ward and backward movement does not occur in each stroke, but only after each stroke displacement step. Since the gear wheel 26 is mounted in fixed position on the drive shaft 25, also its rotation range is shifted in the same manner.

Now if the cam plates 31 and 32 were likewise mounted rigidly on the shaft 25, the curve as such would be shifted in its position with respect to the adjusting slides 33 and 34 and thereby the velocity characteristic would change along the stroke in the course of the entire winding process from stroke to stroke. This may be desired for certain other traverse problems. On the other hand, there are also traverse problems in which the centers of all stroke lengths lie on half winding length, but the ampli-tudes of the traverse movement change on both sides of the central position, as, for example, in the production of winding bodies with stroke reduction. This, too, would be possible without difliculty with the control device represented, with corresponding designed cam plate, as, for example, an Archimedian spiral, for the formation of a conical middle portion of a biconical winding after removal of the detachable stop clamps 37 and 38 as well, possibly, as locking of the slip coupling. In the case of other traverse problems, for example in deck winding with constant reciprocating main stroke and slide displacement of each main stroke toward the one end of the winding taking place in steps or continuously during the entire winding process, the rigid connection of the cam plate 31 or 32 with its drive shaft 25 would, however, frustrate the uniform speed characteristic of each individual stroke.

In consequence, however, of the slip coupling 29 or 30 according to the invention, which produces on the one hand the power connection between the cam plate 31 or 32 with the shaft 25 driving it and, on the other hand, under the action of the stops 37 and 39 or 40 or 38 and 39' or 40', respectively, allows the turning of the cam plate with respect to the drive shaft, difficulties otherwise to be expected, as set forth in the following, are entirely eliminated. The stroke displacement is accomplished for several strokes, in steps or continuously from stroke to stroke by the same amount, in which process now in each case at the end of the main stroke taking place in the same direction as the stroke displacement the stop clamps 37 or 38 strike against the stop pins 39 and 40 or 39' and 40' and arrest the cam plates 31 and 32 in their further turning movement, while the shaft 25 continues to turn with respect to the friction disc 42 and thereby also with respect to the cam plate 31 and 32, respectively, until the stroke displacement span of the total stroke movement going beyond the basic stroke is covered and the stroke reversal takes place. Thereby it is assured that during each individual stroke, in a certain phase always the same cam curve portion activates the appropriate adjusting slide and thereby in the course of the entire winding formation in each stroke there prevails the same velocity characteristic.

The forces necessary for the adjusting of the quanitity regulator 21 or 22 are provided through the torque acting on the drive shaft 25 and must be transferred over the cam plate 31 or 32 to the appropriate shifting lever 33 or 34. -In order to be able to transmit this torque from the drive shaft 25 to the cam plate 31 or 32,. the frictional forces occurring between the collar 45, the friction disc 42 and the pressure washer 43 must be sufficiently great. On the other hand, these forces may be only so slight that the friction disc 42, upon striking of the stop clamp 37 or 38 againstthe stop pin 39 or 39' can turn by sliding with respect to the washer 43 and collar 45, both of which continue to rotate with the drive shaft 25. The contact pressure acting on the elements 45, 43 and 42 is provided by the pressure spring 44. The magnitude of this force can be adapted very easily and precisely to the particular requirements by turning the nut 48 which presses on the spring sleeve 47 with the pressure spring 44 arranged in it.

The changing of the cam plates for plates with any other desired curve characteristics is very rapidly accomplished. In each case only a few screws need to be loosened in order to make it possible to pull off a plate. The inside diameter of the cam plate ring which lies closest to the shaft bearing 28 is greater than the outside diameter of the friction plate carrying the cam plate 32, so that also this cam (curve) plate can be changed relatively quickly and easily without disassembling of the shaft 25.

The stop clamps 37 and 38 can easily be clamped to and unclamped from the cam plates; By resetting the stop clamps, the acting duration or acting stretch of one and the same curve can be changed on the quantity regulator and thereby, correspondingly, also the speed characteristic.

When yarn winding bodies are to be produced in which less value is placed on the inner portion of the Winding, the two quantity regulators can also be controlled in common by one cam plate. Experiments have yielded the result that an especially fine influencing of the winding body form is achieved if, for each controlled quantity regulator, there is engaged in parallel another quantity regulator, with one regulator set permanently for a constant flow-through amount. Likewise, it is possible to restrict oneself in the hydraulic system to the use of a single controllable quantity regulator which, possibly, can be switched parallel with a constant quantity .regulator which is then expediently arranged between pump and reversing slide.

As a control element it is possible, as is represented in FIG. 4, especially where the space-saving arrangement of a cam plate is a less important matter, also to use a fl-at template 50 provided with a cam edge. Template 50 is shiftable longitudinally with respect to its drive element, e.g., thepiston rod 4, and, by means of the stops 51 and 52, which cooperate with the adjustable :stationary stops 53 and 54, can be held fast for a predetermined span of the piston substroke, in which process the template 50 is fastened, for example, to a .shaft :sleeve 55 com-posed of two semicylindrical shells. The :sleeve, by means of leaf springs 56, spring pressure buttons or the like, seated in corresponding recesses, presses against the piston rod 4.

An example of a coupling fixed during the basic stroke and released before the commencement of the stroke displacement span of the sub-stroke is represented in FIG. 5. There the cam plate 50 is held fast by means of the electromagnetic coupling 57 on its drive element, the piston rod 4, and participates in the stroke movements of the piston rod until the coupling is released by the contact of the end switches 58 or 59 with the stops 53 or 54,.so that the piston rod then runs through alone pyer the stroke displacement span going beyond the ing lever 33 or 34 .of the Quantity re ulator 21 .or 22.1

As a further example of the production of a yarn winding by means of the apparatus according to the invention,

an explanation in detail of the buildup of such winding bodies is in order, especially with respect to the control of the quantity regulator, in which the traverse stroke is shortened during the entire winding process from its initially greatest length gradually to a minimum amount, and i to each stroke over an equally long section an equal acceleration course is imparted. In FIG. 7 an arrangement is represented in which the two quantity regulators 21 and 22 are operated by a single control cam 60. The-latter carries t-Wo cam plate curves, but only one stop clamp 61 with the two stop surfaces 62 and 63, to each of which there is allocated a stop pin 64 or 65. For the sake of perspicuity, the connection of the control element 60 with the shaft 25 is not represented but merely indicated by a general type of hub 66. In practice there is used, for example, the slip coupling shown in FIG. .3.

At the beginning of the winding process the stop clamp 61 lies with its stop surface 62 on the stop 64. The

quantity regulator 22 controls the speed of the ring rail 1 in its upward stroke, while the quantity. regulator 21 is 1 out of action. At the commencement of the first stroke, which in the entire winding process is also the longest traverse stroke of the ring rail 1, the-workingpiston 6 according to the cam curve controlling it, at the stroke beginning the greatest passage cross section occurring during the entire stroke. Simultaneously, at the moment at which the working piston 6 begins to move to the left, the control element (cam plate) 60 mounted on the shaft 25 is turned clockwise, the displacing lever 34 is thrust to the left by the control curve cam and the passage cross section of the quantity regulator 22 is slowly but steadily reduced, so that the pressure fluid flowing through, becoming less per time unit, moves the working piston 6 and thereby the ring rail 1 slower and slower, until the shifting lever 34 reaches the arc of the control cam lying concentrically with referenceto the axis of rotation of cam plate 60. From this moment on, then, passage cross section, amount of fluid flowing through and, correspondingly, the stroke speed remain constant, especially since after a certain small angle of rotation of shaft '25 and control element 60 the stop surface 63 strikes the stop 65, so that the control element 6f)v comes to a standstill and thereby the shaft 25, in consequence of yielding to the indicated slip coupling 66, turns with respect to the control element 60. In the longest traverse stroke occurring during the winding body buildup, the slip time of the control element 60 may amount possibly to more than of the total stroke duration.

The shifting lever 33 has reached during the turning of control element 60 clockwise on the control curve (cam) path determinative for it, its starting position for the first downward stroke of the ring rail 1 and waits here until the stroke reversal, Whichis released by the operation of the stroke limiting switch 8 by the switching feeler 7. Working piston 2 60 is now turned counterclockwise by its driveshaft 25. While now the quantity regulator 22 is out of operation, the quantity regulator 21 takes over the control of the speed for the downward stroke, whose speed characteristics should here be equal to those of the upward stroke. After maximum speed at 2 6 is moving to the right and the control element,

the start and gradual retardation, there then follows the section of constant speed until the end of the stroke. The free turning angle of the control element 60 is again exactly as great as in the upward stroke, whereas its slip time becomes less in consequence of the already somewhat shortened stroke. This means that the time from the striking of the stop surface 62 on the stop 64 until the next stroke reversal has become shorter. With diminishing stroke length, the slip duration of the control element 60 and thereby the section of constant speed becomes shorter and shorter from stroke to stroke. The effect that, in the face of this, the acceleration section commencing at the beginning of each stroke remains constant in each stroke is assured through the fact that even the shortest stroke always lasts somewhat longer than the rotary movement of the control element 60 necessary to swing stop clamp 61 from the stop 64 to the stop 65 or vice versa.

With the aid of this apparatus there can be produced also without difiiculty even those winding bodies whose construction begins with the shortest stroke and ends with the longest or in which periods of stroke shortening and stroke lengthening alternate with one another several times.

In a further arrangement, the adjustable quantity regulators 21 and 22 can be mounted on slide-type or carriage-type under-frames 67, by means of which they can be moved on slide or roller tracks 68 toward their con trol elements or away from these. The control of this movement can simultaneously be executed by a drive element which, for example, is executed as a cam plate 69 and turns on its axis during the winding process, in which the appropriate quantity regulator, possibly indirectly or directly under spring pressure of spring 70, bears on the circumference of this cam plate. Through the superimposing of the two control movements, it is possible to control all conceivable acceleration relations along the traverse strokes.

The invention is hereby claimed as follows:

1. A control device for the regulation of quantity flow of hydraulic fluid in a hydraulic traverse drive system of spooling, spinning, ring twist and like filament processing machines comprising a hydraulic traverse drive system, means for supplying hydraulic fluid thereto and exhausting hydraulic fluid therefrom, quantity regulator means to alter the amount of hydraulic fluid flow in said drive system, cam means activating said quantity regulator means, drive means for moving said cam means, and adjustable stop means for limiting the movement of said tivating said quantity regulator means.

2. A control device as claimed in claim 1, reciprocable, hydraulic piston drive means for said hydraulic drive system, reciprocable drive means connected to said piston drive means, drive connection means operatively connecting said reciprocable drive means to said cam means and including a coupling device operable to deactivate said drive connection means upon said limiting of the movement of said cam means by said stop means.

3. A control device as claimed in claim 2 wherein said coupling device is a mechanical, friction-operated, slip clutch.

4. A control device as claimed in claim 3 including, means for adjusting the friction force at which said clutch begins to slip.

5. A control device as claimed in claim 3 including, readily-detachable means mounting said cam means on said slip clutch.

6. A control device as claimed in claim 1 including, releasable means mounting said stop means for adjustment of the position of said stop means.

7. A control device as claimed in claim 1, and means to progressively shorten the traverse stroke of said traverse drive system, and said stop means being positioned relative to said cam means to stop said cam means before the end of all traverse strokes of said traverse drive system.

8. A control device as claimed in claim 1 wherein said cam means includes a single cam element having two camming surfaces respectively activating two quantity regulator means.

9. A control device as claimed in claim 8 wherein the ranges of like camming functions of the said two camming surfaces are arranged to be superimposed on one another.

10. A control device as claimed in claim 1 including, means adjustably mounting said quantity regulator means for setting said last-mentioned means closer to or farther away from said cam means.

References Cited by the Examiner UNITED STATES PATENTS 2,647,698 8/1953 Woolley 24226.1 2,893,354 7/ 1959 Austin et a1. 91-407 2,922,439 1/1960 Pahner 91-405 X 3,130,930 4/1964 Miller 24226.3

FOREIGN PATENTS 626,177 7/ 1949 Great Britain. 706,297 3/ 1954 Great Britain.

STANLEY N. GILREATH, Primary Examiner. 

1. A CONTROL DEVICE FOR THE REGULATION OF QUANTITY FLOW OF HYDRAULIC FLUID IN A HYDRAULIC TRAVERSE DRIVE SYSTEM OF SPOOLING, SPINNING, RING TWIST AND LIKE FILAMENT PROCESSING MACHINES COMPRISING A HYDRAULIC TRAVERSE DRIVE SYSTEM, MEANS FOR SUPPLYING HYDRAULIC FLUID THERETO AND EXHAUSTING HYDRAULIC FLUID THEREFROM, QUANTITY REGULATOR MEANS TO ALTER THE AMOUNT OF HYDRAULIC FLUID FLOW IN SAID DRIVE SYSTEM, CAM MEANS ACTIVATING SAID QUANTITY REGULATOR MEANS, DRIVE MEANS FOR MOVING SAID CAM MEANS, AND ADJUSTABLE STOP MEANS FOR LIMITING THE MOVEMENT OF SAID CAM MEANS TO LIMIT THEREBY THE EFFECTIVE CAM PORTION ACTIVATING SAID QUANTITY REGULATOR MEANS. 